Dynamoelectric machine

ABSTRACT

Rotatable assembly of dynamoelectric machine is provided with at least one spacer that is collapsed from an initial length, in its free form, to a preselected length in its final configuration, to provide means for controlling end play of the assembly and for establishing a desired alignment of the assembly with the stationary structure of the machine. Collapsing the spacer reduces an internal diameter of the spacer and rigidly secures the spacer to a shaft portion of the assembly. Axial length of a thrust member is reduced to a preselected length relative to a reference portion of a rotatable assembly and the length of a second thrust member may also be reduced to establish a preselected distance between two thrust surfaces. Disclosed apparatus includes a pair of opposed rams having spacer collapsing tooling that includes anvil means for collapsing the spacers and abutment means for engaging other portions of a rotatable assembly. A lost motion mechanism interconnects one of the anvil means and one of the abutment means.

United States Patent [1 1 Busian 1 1 Sept. 30, 1975 [73] Assignee: General Electric Company, Fort Wayne, 1nd.

221 Filed: June 28,1973

21 App]. No.: 374,409

Related US. Application Data [62] Division of Ser. No. 211,575, Dec. 23, 1971, Pat. No. 3,786,561, which is a division of Ser. No 40,224, May 25, 1970, Pat. No. 3,681,836.

[52] US. Cl 310/42; 310/90 [51] Int. Cl. HOZK 15/00 [58] Field of Search 310/90, 40 MM, 85, 91,

Tupper 308/127 Schulze 310/90 Primary Examiner-R. Skudy Attorney, Agent, or Firm-Ralph E. Krisher, Jr.

[5 7 1 ABSTRACT Rotatable assembly of dynamoelectric machine is provided with at least one spacer that is collapsed from an initial length, in its free form, to a preselected length in its final configuration, to provide means for controlling end play of the assembly and for establishing a desired alignment of the assembly with the stationary structure of the machine. Collapsing the spacer reduces an internal diameter of the spacer and rigidly secures the spacer to a shaft portion of the assembly. Axial length of a thrust member is reduced to a preselected length relative to a reference portion of a rotatable assembly and the length of a second thrust member may also be reduced to establish a preselected distance between two thrust surfaces. Disclosed apparatus includes a pair of opposed rams having spacer collapsing tooling that includes anvil means for collapsing the spacers and abutment means for engaging other portions of a rotatable assembly. A lost motion mechanism interconnects one of the anvil means and one of the abutment means.

5 Claims, 12 Drawing Figures Sheet 2 of 3 a m x. a

ll 7 1. mull!!! Q g S US. atent Sept. 30,1975

FICIS App/129a For-ca (pounds) .078 .ns J58 J98 1250 .278 .318 .358 .599 .459 .500 Spacer Length-(inches) DYNAMOELECTRIC MACHINE v CROSS REFERENCE TO RELATED 1 APPLICATIONS This is a division of my copending application Ser; No. 211,575, filed Dec. 23, 1971, now US. Pat. No. 3,786,561; which application in turn is a division of my then copending application Ser. No. 40,224, filed May 25, 1970, now US. Pat.No. 3,681,836.

BACKGROUND OF THE INVENTION This invention relates generally to machines wherein two or more component parts are assembled together inpredetermineddimensional relationship, and, more particularly, to machines wherein one such component part is provided with one or more surface regions that are spaced preselected distances from reference por-' tions of the component.

Satisfactory preformance of diverse types of machinery is usually dependent on component parts of the machinery being assembled together with sepecified dimensional tolerances. In the case of rotable machines, such as, for example, dynamoelectric machines, a rotatable member is assembled with a stationary member so that during normal operation there will be little or no relative movement between the members along the rotational axis of the machine.

In electric motors, this relative movement is often referred to as end play. When excessive, end play may have a pronounced effect of the operation of a device being driven, as described, for example, in Thompson et al. US. Pat. No. 3,020,105 which issued Feb. 6', 1962 and which is assigned to the assignee of this patent application.

Accordingly, efforts have been made to reduce, if not eliminate, end play by using cured thermosetting resins positioned between ashoulder on a shaft and a stationary thrust member. Another approach has involved the use of combinations of shim washers of different thickness that are selected on a trial and error basis. This approach is referred to in Wightman US. Pat. No. 2,539,879, dated Jan. 30. 1951. These shim washers have been used at one or both ends of a rotatable member to hold it in a desired nominal position between a pair of bearings.

An approach suitable for use in a unit bearing type motor isdescribed in the Wightman patent as involving the use of a single standard thickness thrust washer positioned between a shoulder on arotor shaft and the outboard end of the unit bearing, and the use of an inboard washer member crimped against grooves on the inboard end of the rotor shaft. In this latter approach, the inboard washer has been assembled on the shaft after the rotor has been assembled with the bearing and after a desired amount of end play has been established. Still other approaches are described in Bussone ment where a rotor is constrained at the time of assembly to a precise location relative to one or more bearings,-the self-centering action of an improperly aligned rotor may contribute to increased frictional engagement of parts of the motor thrust system and, in aggravated cases, measurably decrease the efficiency of the motor in addition to accelerating wear of the thrust system.

Although the above described approaches of using crimped washers and thermosetting resins have been improvements in the art, they have still been expensive to implement in practice. In addition, while providing a means'for limiting rotor shaft end play relative to one or more bearings, these approaches, in practice, have not provided an economical means for accurately alignming and centering a rotor relative to the magnetic material of a stator. I

On the other hand, the practice of placing combinations of shim washers of different thicknesses at each end of a rotor prior to assembly with a stator is prohibitive in cost; This is due to the fact that several different thicknesses of shim washers must be stocked, and measurements must be made to determine what combination of shim washer thicknesses would be needed to establish a shim washer surface at a preselected distance from a reference portion of the rotor or rotor shaft. In addition, previously positioned loose washers may literally fall off the rotor shaft prior to final motor assembly in the absense of special handling procedures or additional means for holding the shim washers in place on the rotor shaft.

Because of the various subjective determinations that must be made when using the shim washer approach, the time required for shimming each end of a rotor and the opportunity for errors in operator judgement is relatively great. On the other hand, the other practical approaches referred to in the above referenced patents have also been expensive in practice.

It will therefore be understood that it would be desirable to provide an improved arrangement for restricting end play of a rotor shaft. It also would be desirable to such an arrangment that is conducive to consistently and economically establishing one or more surface regions on a rotatable assembly fo a dynamoelectric machine at preselected distances from a reference portion of the assembly. In addition, it would be desirable to provide such an arrangement whereby means are provided that may be used to control shaft end play and that may also be used to center a rotatable member. relativeto a stationary member;

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide an improved assembly having means for restricting the end play of a rotatable shaft.

Another'object of the presentinvention is to provide an improved dynamoelectric machine and an assembly for use therein having means for restricting the end play of a rotatable shaft and for aligning the assembly with the stationary magnetic structureof the machine.

A further object of the present invention is to provide an improved arrangement wherein one or more surface regions on a dynamoelectric machine component are located at a preselected distance from one or more reference portions of the component.

In carrying out these objects, in one form, there is provided an electric motor including a stationary magnetic structure, a pair of end frames carrying shaft supporting bearings, and a rotatable assembly. In a preferred form, the rotatable assembly includes a shaft, a conventional rotor supported on the shaft, and spacer means for restricting the end play of the rotor relative to the stationary magnetic structure. In a specific form, these spacer means form part of the motor thrust system and also are useful for establishing a predetermined alignment between the rotor and stationary magnetic structure. These spacer means, in an illustrated form, include a spacer or sleeve rigidly secure to and forming a part of the rotatable assembly.

A first one of the spacers has a surface region spacer a first preselected distance from a reference portion of the rotor, e.g., an end lamination of a laminated rotor core. A second spacer has a surface region spaced a second preselected distance from the surface region of the first spacer. These surface region locations are determined by collapsing the spacers longitudinally along the shaft to establish a desired final configuration of the spacers. The internal diameter of the spacers is reduced by collapsing the spacers and the internal surfaces of the spacers press against the shaft to rigidly secure the spacers to the assembly. This assembly, other components of the thrust system, end frame supported bearings, and a stator are then assembled to form a complete dynamoelectric machine.

. In one preferred approach, a spacer is placed on an end of a rotor shaft and a surface region of the spacer is deformed longitudinally along the shaft toward the rotor core which was previouslysecured to the shaft. The spacer is stressed and deformed until the surface region of the spacer is in a desired preselected position relative to the corer and until the spacer is deformed into a final configuration so as to secure it to the shaft. In the preferred approach, a spacer is deformed on each end of the shaft, with a first spacer being formed initially on one side of the core as just described. Then the surface region of the first spacer is used as a reference portion of the rotatable assembly while a second spacer is deformed to a desired final configuration on the other side of the core.

The preferred approach for securing together an assembly for use in the manufacture of a dynamoelectric machine may be accomplished with apparatus that includes a pair of opposed double acting hydraulic rams with double end rods. In such apparatus, each rod is provided with an anvil forming part of the tooling of the apparatus and which engages a spacer on a rotatable assembly, including a rotor core, while the spacers are axially compressed between the two rams. A fixed abutment and a movable abutment engage opposite end faces of the core. The movable abutment moves with one of the rods and is secured thereto by a spring biased lost motion linkage. The movable abutment, the fixed abutment, and both anvils coact to collapse one spacer and hold the core in a fixed position. Thereafter, one anvil and the two abutments coact to collapse the other spacer.

The subject matter which I regard as my invention is particularly pointed out and distinctly claimed in 'the concluding portion of this specification. My invention, itself, however, both as to its organization and method of operation, together with further objects and advantages thereof, may best be understood by reference to the following description taken in connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded perspective view of a dynamoelectric machine constructed in accordance with one form .of the invention and embodying the invention in one form with parts broken away and apart shown in its free form for the purpose of illustration;

FIG. 2 is a side elevational view, with parts broken away, of the rotor shown in FIG. 1;

FIG. 3 is a side elevational view, partly in section and with parts broken away,'of an end of the rotatable assemblyshown in FIG. 2, with a spacer shown in its free form prior to being deformed to a final configuration and secured to the rotatable assembly;

FIG. 4 is a viewsimilar to FIG. 3 with the spacer of FIG. 3 compressed longitudinally along the rotor shaft axis to its final configuration;

FIG. 5 is a perspective view, with parts broken away and parts removed, of an apparatus'that may be used in a preferred approach;

FIG. 6 is a perspective view, with parts broken away, of the apparatus of FIG. 5 during operation of the apparatus;

Flg. 7 is a side elevational view, in cross section, of the apparatus shown in FIG. 5 at the beginning of one cycle of operation of the apparatus;

FIG. 8 is a view similar to FIG. 7 showing the apparatus during a cycle of operation;

FIG. 9 is a view similar to FIG. 7 showing the apparatus as one cycle of operation as being completed;

FiG. 10 is a view similar to FIG. 8 showing another embodiment of the apparatus during the part of the operational sequence corresponding to that illustrated by FIG. 8;

FIG. 11 is a graph showing representative spacer lengthsapplied axial forces for spacers of the type and sizes shown in the FIG. 1 embodiment; and

FIG. 12 is a schematic representation of a control circuit that may be usedto establish an operational sequence of the apparatus shown in FIG. 5.

DESCRIPTION or THE PREFERRED EMBODIMENTS Turning now to the drawings in more detail, and in particular to FIGS. 1 through 4, one form of the present invention is illustrated as being incorporated in a double shaft, band mount type of induction motor 20 comprised of a stator 21, end frames 22, bearings, a rotatable assembly 23, and a thrust system.

The rotatable assembly includes the shaft 24, a conventional short circuited squirrel cage winding and laminated magnetic core 28 comprised of a stack of laminations 29 which collectively will be referred to hereinafter as a rotor. Conductor bars 33 and end rings 34 are illustrated as having been formed of a suitable electrically conductive material, such as aluminum, in a die cast process. The rotatable assembly 23 also includes means for controlling the end play of the rotor when it is assembled with the stator 21 and these means are illustrated as comprising cylindrical spacers or sleeves 36 and 37.

As will be appreciated from FIG. 1, the spacers 36, 37, have surface regions which are defined by the flanges 38, 39 and may be used as thrust members. These surface regions are located preselected distances relative to the end lamination 41 of the rotor core and relative to each other as will be more thoroughly described hereinafter. For purposes of illustration in FIG. 1, the thrust member 37 is shown in its free form prior to being deformed and rigidly secured to the shaft 24 to form part of the rotatable assembly 23.

The illustrated embodiment includes thrust members 42 which abut the surface regions of the flanges 38, 39. The thrust members 42 are similar to the thrust members disclosed in the above identified Bussone patent. Also included is a pair of star springs 43 of the type dis closed in the Myron D. Tupper U.S. Pat. No. 3,038,765 which issued June 12, 1962 and is also assigned to the assignee of the present invention. Thrust washers 44 are provided between the star springs 43 and the surfaces of the bearings carried by the end frames 22.

As previously indicated, it is desirable for a number of reasons to limit or control the amount of end play of the rotor relative to the stator during the operation of the motor 20. Also as will be appreciated from the above background of the invention, it is very desirable to provide for the relatively precise centering or alignment of the magnetic portion of the rotor'assembly, i.e., the stack of magnetic laminations 29, relative to the magnetic portion of the stator 21, e.g., the stack 46 of stator laminations.

The stack heights of magnetic laminations vary from stack to stack because of normal manufacturing tolerances. In order to compensate for such variations, I have provided means for restricting the end play of the rotor relative to the end frames and for economically establishing a desired alignment between the rotor and stator.

' In the illustrated embodiment, these means comprise the spacers 36, 37. With reference to FIG. 3, it will be appreciated that the spacer 36, in its free form, has the configuration of a flanged cylinder. This is also the configuration of the free form of spacer 37 which for purposes of illustration is shown in its free form in FIG. 1.

FIG. 4 shows the final form or configuration of the spacer 36.after it has been deformed and rigidly secured to the shaft 24. The final configuration of the spacers 36 and 37 is attained by applying an axial force against the flanges of the spacers to reduce the longitudinal or axial length of the spacers. This force causes the spacers to collapse and reduces at least portions of the internal diameter of the spacers. FIG. 4 clearly shows the collapsed condition andfinal configuration of spacer 36 with an undulated surface as shown at 51. Although the sleeve 36 tightly engages the shaft 24, it will be understood that engagement of the shaft and spacers is not necessary for the practice of my invention. I

By collapsing the spacers preselected amounts, precise alignment of the rotatable and stationary magnetic material may be attained. With reference to FIG. 2, it will be appreciated that the over-all dimension or distance A between the surface regions of flanges 38, 39 is preselected to control the amount of end play of the rotor. However, simply holding this dimension A to a prescribed nominal preselected value would not assure proper alignment between the rotor and stator iron during operation of the motor 20. The alignment of these parts may, however, be controlled by preselecting and holding the dimension or distance B between the surface region of the flange 39 and a reference portion of the rotatable assembly such as the face of the end lamination 41.

In the manufacture of the rotatable assembly 23, I loosely position the spacer 36, 37 on the shaft 24 in their free form as indicated by the plantom line position of the spacers in FIG. 4. Then I collapse the spacer 37 to the position shown in full in FIG. 2 an amount just sufficient to establish the flange surface region of the spacer 37 at the preselected distance B from the face of the end lamination 41. 1

After establishing the location of the surface region of the spacer 37, I collapse the sleeve 36 to the final configuration shown by solid lines in FIG. 2 and as shown in FIG. 4. The spacer 36 is collapsed along the shaft 24 until the over-all distance, corresponding to the distance A, is equal to the preselected distance whichwill yield the desired controlled amount. of end P y- It will be appreciated that, one approach that may be followed includes collapsing a spacer against a shaft in order to rigidly secure the spacer to a rotatable assembly and establish a surface region at a precise axial location along a shaft.

FIGS. 5 through 9 illustrate apparatus that may be utilized in the approach just mentioned to manufacture a dynamoelectic machine and more particularly for use in securingtogether a rotatable assembly such as the rotatable assembly 23 shown in FIG. 1.

The over-all arrangement of the apparatus 71 is best revealed in FIG. 5. The apparatus 71 includes a frame 72, a double acting hydraulic ram 73 with a double end rod 74 (best shown in FIG. 7, a double acting hydraulic ram 76 having a double end rod 77, and control means which will be described hereinafter in connection with FIG. 12. I

The rams 73 and 76 are secured by any suitable means such as bolts, studs, or welds to the frame 72 and areoppositely disposed in facing relationship at opposite ends of the frame 72. a

First and second tooling assemblies are provided for receiving the ends 25, 26 of the shaft 24. One of these tooling assemblies includes an anvil carried by the rod 74 of the cylinder 73 and abutment means illustrated as a pressing head having an abutment surface 78 forenga'ging the surface of the end lamination 52. This tooling assembly also includes lost motion means for interconnecting the abutment surface 78 and anvil 75. The exemplified lost motion means includes a retaining color 79 secured to the rod 74 by suitable means suchasone or more set screws or a weld bead,

a spring retaining ring 81, a coil spring 82 and a flange 83 of the pressing head 80.

The other tooling assembly includes abutment means in the form of a fixture 87 secured by bolts or other suitable means to the bed 88 of the frame 72. The fixture 87 has an abutment surface 89 for engaging the surface of the end lamination 41 of the assembly 23, and an anvil 91 adapted to engage surface regions of the sleeve 37.

In preparation for operation of the apparatus 71, the sleeves 36, 37 are loosely assembled on the shaft 24 and,-'with the rams 73, 76 in their retracted positions, the rotatable assembly 23 is positioned with the lower end 26 of the shaft positioned in the fixture 87 and extending through a bore in the anvil 91 and rod 77. Then a control circuit is actuated and low pressure hydraulic fluid raises the lower rod 77 to the position shown in FIG. 7. At this same time, the upper rod 74 moves at a low power levelto the position shown in FIGs. 6 and IntheiFIG. 7 position, the'sleeve 37 is supported on theariyil9l with the end lamination 41 spaced from the abutment surface 89. The anvil 75 of the upperto'olin'g assembly, however, is. spaced from the sleeve 7 36 whereas the abutment surface 78- of the pressing head 80 is in engagement with the surfaceof the end lamination 52% At this point in'the operational cycle of the-apparatus 71, hydraulic fluid under high pressure is applied to theram's 73 and 76 to establish an"increased power level as will be described more fully hereinafter in the discussion of FIG. 11.

As the high pressure fluid is admitted to the cylinders, the lower rod 77 is retained in its extreme upward position as shown in each of FIGS. 7, 8 and 9. In addition, the upper rod 74 moves downwardly and moves through a lost motion increment of travel relative to the pressing head 80 while compressing slightly the compr'ession spring-82. The spring 82 in the embodiment of FIGS. 7-9 is sufficiently weak that the spring is compressed during the lost motion travel of rod 74 and neither of the spacers 36, 37 are collapsed at'this time. However, as the anvil 75 engages the spacer 36, the combined force exerted by the anvil 75 and pressing head 80 is sufficient to move the assembly 23 against the lower abutment surface'89 of the fixture 87. This movement collapses the spacer 37 to the preselected length identified by the distance B in FIG. 8.

It will be noted that the spacer 37 is collapsed prior to distortion of or collapse of the spacer 36. The upper spacer 36 is not collapsed at this time since the total downward force applied to the spacer 36 is equal only to the force exerted by the anvil 75, and'this force is equal'to the difference between the downward force of the rod 74 and the force exerted by the pressing head 80 against the lamination 52. As the end lamination 41 seats 1 against the abutment surface 89, the pressing head 80 is restrained from further movement by the end lamination 52. This condition is illustrated by FIG. 8. However, the anvil 75 then moves through a second increment of lost motion travel relative-to. the pressing head 80 and exerts sufficient force to collapse the spacer 36 to the final configuration shown in FIG. 9. At this time, the distance A is established between the selected surface regions of the spacers 36, 37.

The spacer 36 is collapsed until the rod 74 reaches its lower limit of travel and, at this time, the apparatus 71 is recycled, the rod 74 returns to its retracted position, the spring 82 expands and establishes the relative position between the pressing head 80 and anvil 75 as shown in FIGS. and 7, and the lower rod is free to move to its retracted position. In the rest position,

screw 70 retains the pressing head 80 in assembled relation'with the rod 74.

It will be'understood that the distance B of FIGS. 8 and 9 is determined by the extent of upward travel of the anvil 91 secured to the lower rod 77 and that, after the distance B has been established, the over-all dis-' The limits of travel of the rods 74 and 77 are determined by simple adjustments which are most readily described by again having reference to FIG. 5. In FIG. 5 it will be seen that the maximum downward travel of the. rod 74 is limited when an adjustable stop nut 95 carried by the upper end of the rod 74 engagesthe adjustable stop 96 supported at the outer end of the cylinder .73. A fine adjustment of the travel of rod 74 may be made by moving the stop nut 95 along the threaded portion of the shaft 74,,whereas a course adjustment of rod travelreadily. may be made by changing the length of pairs of split sleeves 97. This type of change is readily accomplished by raising the spacer retaining ring 98, removing the split sleeves and replacing them with longer or shorter sleeves. Thereafter, the retaining ring 98 is again dropped into place to lock the split sleeves in place at the top of. the ram 73 as shown in FIG. 5 It will be understood that this type of course adjustment is normally madewhen it is desired to secure spacers to a rotatable assembly having a different stack height of laminations than the stack height for the rotatable assembly 23. g

I The upward travel of the lower rod 77 is adjusted and determined by a stop nut, split sleeves, and a retainer ring substantially identical to those shown in FIG. 5. Since the means for adjusting the travel of the lower rod 77 is substantially the same as the means used for adjusting the travel of the upper rod 74, these means have not been illustrated in the drawings.

Now having reference to FIG. 10, a modified form of the apparatus 71 will be described. The apparatus represented by FIG. 10 is identical in all respects to the apparatus 71 with the exception that the spring 101 is stiffer than the spring 82.

With this modification the point of time during'the operational cycle of the apparatus represented by FIG. 10 corresponds to the point of time in the operational cycle represented by FIG. 8, i.e., the lower sleeve 37' is collapsed to its final configuration and the end lamination 41 is resting against the lower abutment surface 89. It will be noted from FIG. 10, however, that the anvil has not yet engaged the spacer 36. This is caused by the fact that, with the stiffer spring 101, the force required to compress the spring 101 and effect a lost motion increment of travel of the anvil 75 relative to the pressing head is greater than the force required to collapse the not shown spacer 37.

With the modification of FIG. 10, continued downward travel of the rod 74 from the position shown in FIG. 10, will effect a lost motion increment of travel of the anvil 75 relative to the pressing head 77 and cause the pressing head and anvil to be relatively positioned in exactly the same manner as illustrated in FIG. 9 at the end of the operational cycle of the apparatus.

Thus, it will be understood that the stiffness of the springs '82 and 101 is not critical. Furthermore, it is only desirablethat sufficient total force be applied to one sideof the rotatable assembly to effect the preselected amount of crushing of the spacer disposed on the.

other side of such assembly. Therefore, the abutment means at either side of the rotatable assembly may be interconnected to the anvil on that same side of the assembly through any suitable lost motion connection.

I Furthermore, if the advantage of being able to adjust the preselected distances B and A is not deemed to be desirable, one of the anvil means may be rigidly secured to one of the abutment means. For example, if it is not desired to adjust the preselected distanceB, the lower ram 76 may be eliminated and the anvil 91 may be rigidly secured to and form a part of the fixture 87 having an abutment surface 89 and being at least a part of an abutment means as previously described.

In those applications where it is not desired to provide the flexibility afforded by changing the distance A, the upper anvil 75 may be rigidly secured to the pressing head 80 with the distance between the abutment surface 78 and the striking surface of the anvil 75 being fixed to correspond to the desired final length of the upper spacer 36. In this case'the, assuming that it were desired to collapse the upper spacer 36 prior to collapsing the lower spacer 37, the anvil 91 could be rigidly secured to the bed 88 as a fixture, and the lower abutment surface 89 could be interconnected with the bed 99 and anvil 91 through a lost motion mechanism.

Turning now to FIG. 11, there is shown a graph of spacer length versus collapsing force for a pair of spacers of the type and size of spacers 36, 37. The original traces for the curves depicted by the FIG. 11 graph were obtained by positioning spacers similar to the spacer 36, 37 on a shaft similar to the shaft 24 of the motor 20 and applying a force against the flange end of the spacer while compressing the sleeve against a stop plate. The actual force, in pounds, exerted against the test spacers and the actual length of the spacers was continuously recorded with an X-Y recorder. In FIG. 11, the trace identified by the letter L is typical of the traces that were obtained with the recorder for the relatively longer spacers, e.g., the spacer 36; and the trace S is typical of the traces that were obtained during testing of specimens corresponding to relatively short spacers, e.g., the spacer 37.

It will be appreciated from an inspection of the traces S and L that after an initial peak force was applied to each test spacer that length of the spacers rapidly decrease while the applied force decreased until a lower limit of applied force was reached. These peak points are identified as points D and E in FIG. 11. The dips in the traces, e.g., from D to F on trace L, occurred as the test spacers collapsed.

Flg. 11 clearly reveals that the applied force required to collapse the test spacers a given amount was approximately the same for all samples tested. The data presented by the FIG, 11 curve is useful in determining the suitability of different types of spacers for use in various motor applications. For example, the spacers 36, 37 are suitable for use in applications where the end thrust applied to the motor shaft by a load is not expected to be in excess of about 200 pounds.

The FIG. 11 data is also useful in determining the amount of spacer collapsing force that could be used in the preferred approach as well as in the use of apparatus such as the apparatus 71 shown in FIGS. through 10. For example, in the illustrated embodiment, the shorter spacer 37 is collapsed to establish the preselected distance B. So long as the applied force exceeds 900 pounds, it is clear from FIG. 11 that either the spacer 37 or spacer 36 can be collapsed to substantially any desired length.

As previously mentioned, the test spacers corresponded to the spacers 36 and 37. By way of exemplification, the spacers were made of common steel, had an outer diameter of 0.335 inches, a wall thickness of 0.010 inch, and would freely slide over a 0.3125 inch diameter rod, this being the nominal diameter of the shaft 24 in'the exemplification. All of the spacers had a flange with an outer diamter of .500 inch and an inner diameter of the same as the inner diameter of the spacer. The flange thickness was 0.010 inch. The free length of the spacers was nominally 0.250 inch for the spacer 37 and 0.500 inch for the spacer 36. Although steel spacers were used for purposes of exemplification, it will be expressly understood that any other material having satisfactory force-deflection or forcedeformation characteristics may be used to form the spacers. Furthermore, the shape of the spacers may be generally cylindrical as illustrated or other suitable shapes.

Turning now to FIG. 12, there is shown a schematic representation of a control circuit that may be used as a control means for effecting the operational sequence of the apparatus 71 illustrated in FIGS. 5 through 10. To facilitate correlation of figures of the drawings, identical numbers have been used, where appropriate, for the schematic symbols that correspond identically with structural elements in FIGS. 5 through 9. Thus, the rams 73, 76 and rods 74, 77 are identified with those numerals in FIG. 5 and in FIG. 12.

In order to begin operation of the apparatus 71, the manual shut off valve 101 located at the inlet of the upper ram 73 is opened. Then, valve 102 is open to connect the control circuit of FIG. 12 with an psi air supply. Air, which is used in various timing portions of the control circuit is passed through an air filter 103, an air pressure regulator 104 to reduce the air pressure to a desired nominal value of 30 psi, and a conventional air lubricator 106.

With valves 101 and 102 open, and the apparatus 71 in a rest or dwell condition, air is supplied through line 107, four-way double air-pilot operated detented valve 108 and line 109 to the lower part of ram 73. The air supplied to ram 73 at this time holds the rod 74 in a retracted or upper position. Air is also supplied through line 110 to a conventional 25:1 hydraulic booster 111 with attached reservoir 112. The air supplied by line 110 holds the high pressure ram of the booster 111 in an up or temporarily inactive position. The upper port of the ram 76 is vented to atmosphere through line 113 at all times and, while in the rest position, the rod 77 is free to move downwardly as viewed in FIGS. 5-9 and FIG. 12. 7

After the rotatable assembly 23 has been positioned as described in connection with FIG. 7, the operational sequence of the apparatus 71 is initiated by temporarily closing finger tip air valve 114 which normally bleeds air to the atmosphere. When closed, valve 114 supplies regulated air through line 115 to the dented air-pilot 116v of. valve 108. This in turn causes the valve 108 to shift, vent line 1 l7 (and accordingly lines 109 and 110) to atmosphere, discontinue the venting of llne 118 to the atmosphere, and connect line 107 to line 118.

At this time, regulated air is supplied to lines 119, 121, and 122. The air in line 119 enters the oil reservoir 112 and forces oil under low pressure) through a bypass valve through line 124 to the bottom of booster cylinder 111, and through lines 124 and 126 to the rams 73 and 76. The low pressure oil drives the rods 74 and 77, at a relatively low power level, to the position shown in FIG. 7. This provides the advantage of reducing the hazard of damage to equipment and personnel in the event that the shaft is not properly received in the upper tooling assembly.

While air is moving through line 119 to the reservoir 112, air also is moved through line 122 to a timing device comprised of a flow control valve 127 and an air reservoir 128 connected thereto by line 129. The purposeof this timing device is to delay the supply of high pressure hydraulic fluid to the rams 73, 76 until the abutment surface 78 and anvil 91 have firmly seated against the rotatable assembly 23 as shown in FIG. 7.

Returning again to FIG. 11, after a predetermined time, determined by the flow rate through adjustable valve 127 and the capacity of air reservoir 128, sufficient air pressure will exist in line 131 to actuate the air-pilot 132 of air-pilot operated spring return valve 133. As valve 133 is actuated, line 134 ceases to vent to the atmosphere, and air line 121 (now connected to line 107 through valve 108) is connected to line 134.

Upon completion of this connection, regulated air is supplied to the upper port of the booster cylinder 111 through line 136 and through line 137 to another timing device comprised of the flow control valve 138. As air is admitted to the upper port of the booster 111, the by-pass valve of reservoir 112 is closed, and high pressure oil is fed through lines 124 and 126 to the rams 73, 76 and thereby establishes an increased power level for operation of the apparatus 71.

In the arrangement just described, the high pressure oil was sufficient to impart a crushing force of 1500 pounds to rod 74 which had a rod diameter of 1% inches disposed in the 2 /2 inch bore of ram 73. The ram 76, on the other hand, had a two-inch bore and rod diameter of 1 inch. The piston area of the rams, as will be understood, was the difference between the crosssectional area of the ram bore and rod diameter.

The high pressure oil is supplied via lines 124 and 126 for a sufficient period of time (actually, less than 1 second) to complete the operational sequence represented by FIGS. 8 and 9. The actual duration of this period is adjustable and determined by the adjustable flow control valve 138 since valve 138 provides a delay in the application of full regulated air pressure to the detented air-pilot 139 of valve 108. After the desired time interval, air-pilot 139 resets valve 108 to the original position as illustrated, whereupon line 109 is again supplied with air from line 107 and line 118 is again vented to atmosphere. As this occurs, spring 141 resets valve 133 and line 134 also vents to atmosphere. One cycle of operation of the apparatus 71 is then completed as the booster 111 and valve 138 vent to atmoing mechanical and electro-mechanical means may be used to power the anvil means and abutment means of the apparatus 71 when practicing the invention. Also, electrical, mechanical, or electromechanical devices may be used in place of the pneumatic portions of the control circuit shown in FIG. 12.

It will be seen from the foregoing that the present invention provides an improved dynamoelectric machine structure.

1 While the invention has been explained by describing preferred embodiments thereof, it will be apparent that improvements and modifications may be made without departing from the scope of the invention as defined in the appended claims.

What I claim as new and desire to secure by Letters Patent of the United States is:

1. A'dynamoelectric machine comprising a stationary magnetic structure and a rotatable assembly including a shaft supported for rotation relative to the stationary magnetic structure and a rotatable magnetic structure secured to the shaft, the rotatable assembly further including spacer means for restricting end play of the rotatable assembly relative to the stationary magnetic structure and for aligning the rotatable and stationary magnetic structures relative to one another, said spacer means comprising at least one spacer in the form of an integral tubular sleeve mounted about the shaft and having an axial length when mounted about the shaft less than its length in its free form, said spacer having a buckled portion when mounted about the shaft with at least one undulation along the buckled portion rigidly securing the spacer as a part of the rotatable assembly. I

2. The dynamoelectric machine of claim 1 wherein said at least one spacer comprises a compressed member having a surface region spaced a preselected distance from a reference portion of the rotatable assembly.

3. A rotatable assembly for a dynamoelectric machine having a stationary magnetic structure said assembly comprising a shaft, a magnetic core secured to the shaft, and means for restricting end play of the assembly relative to a'stationary magnetic structure, said means for restricting end play including a rigid thrust member in the form of an integral tubular sleeve mounted about the shaft and having a buckled portion in rigid engagement with at least one part of the assembly, said rigid thrust member having a portion thereof bearing against a thrust member engaging surface of the assembly and having a surface region spaced a preselected distance from a reference portion of the assembly, the location of the surface region being determined by the application of a collapsing and buckling force thereto while said portion of the thrust member is bearing against the thrust member engaging surface of the assembly.

4. The rotatable assembly of claim 3 wherein the thrust member engaging surface comprises the reference portion of the assembly and the rigid thrust member comprises a spacer carried by the shaft, the spacer being collapsed in an axial direction an amount equal to the diffemce between the free length of the spacer in an uncollapsed condition and said preselected distance.

5. The rotatable assembly of claim 3 wherein the thrust member comprises a spacer having an axial length and internal diameter, when mounted about the shaft, less than the axial length and internal diameter thereof while in a free form prior to assembly. 

1. A dynamoelectric machine comprising a stationary magnetic structure and a rotatable assembly including a shaft supported for rotation relative to the stationary magnetic structure and a rotatable magnetic structure secured to the shaft, the rotatable assembly further including spacer means for restricting end play of the rotatable assembly relative to the stationary magnetic structure and for aligning the rotatable and stationary magnetic structures relative to one another, said spacer means comprising at least one spacer in the form of an integral tubular sleeve mounted about the shaft and having an axial length when mounted about the shaft less than its length in its free form, said spacer having a buckled portion when mounted about the shaft with at least one undulation along the buckled portion rigidly securing the spacer as a part of the rotatable assembly.
 2. The dynamoelectric machine of claim 1 wherein said at least one spacer comprises a compressed member having a surface region spaced a preselected distance from a reference portion of the rotatable assembly.
 3. A rotatable assembly for a dynamoelectric machine having a stationary magnetic structure said assembly comprising a shaft, a magnetic core secured to the shaft, and means for restricting end play of the assembly relative to a stationary magnetic structure, said means for restricting end play including a rigid thrust member in the form of an integral tubular sleeve mounted about the shaft and having a buckled portion in rigid engagement with at least one part of the assembly, said rigid thrust member having a portion thereof bearing against a thrust member engaging surface of the assembly and having a surface region spaced a preselected distance from a reference portion of the assembly, the location of the surface region being determined by the application of a collapsing and buckling force thereto while said portion of the thrust member is bearing against the thrust member engaging surface of the assembly.
 4. The rotatable assembly of claim 3 wherein the thrust member engaging surface comprises the reference portion of the assembly and the rigid thrust member comprises a spacer carried by the shaft, the spacer being collapsed in an axial direction an amount equal to the differnce between the free length of the spacer in an uncollapsed condition and said preselected distance.
 5. The rotatable assembly of claim 3 wherein the thrust member comprises a spacer having an axial length and internal diameter, when mounted about the shaft, less than the axial length and internal diameter thereof while in a free form prior to assembly. 